US8740569B2 - Impeller for a centrifugal pump - Google Patents

Impeller for a centrifugal pump Download PDF

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Publication number
US8740569B2
US8740569B2 US12/714,626 US71462610A US8740569B2 US 8740569 B2 US8740569 B2 US 8740569B2 US 71462610 A US71462610 A US 71462610A US 8740569 B2 US8740569 B2 US 8740569B2
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Prior art keywords
blades
impeller
blade
shroud
impeller according
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US12/714,626
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US20100226773A1 (en
Inventor
Aage Bruhn
Lars Ostergaard
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Grundfos Management AS
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Grundfos Management AS
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Assigned to GRUNDFOS MANAGEMENT A/S reassignment GRUNDFOS MANAGEMENT A/S ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OSTERGAARD, LARS, BRUHN, AAGE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape

Definitions

  • the present invention relates to an impeller for a centrifugal pump.
  • Impellers for a centrifugal pump typically include at least a carrier body, typically of a carrier disk, and blades arranged thereon.
  • the carrier disk is thereby regularly designed for the rotationally fixed arrangement on a shaft.
  • the impeller blades depending on the construction type, lie exposed (open impeller) or covered by a shroud, which lies opposite the carrier disk and is connected to the blades.
  • the impellers are known in different construction forms and are applied in single-stage or multistage centrifugal pumps.
  • the impellers typically comprise two or more impeller blades, which may be designed and/or arranged in an equal manner or also in a differing manner.
  • the impeller represented in FIG. 1 comprises a circular carrier disk 1 , which comprises a central recess 2 , which is profiled and is envisaged for the rotationally fixed connection to a drive shaft (not shown), as is counted as belonging to the state of the art with centrifugal pumps.
  • a multitude of impeller blades 3 is arranged on the carrier disk 1 , which extend at a distance to the recess 2 , up to the outer periphery of the carrier disk 1 .
  • the blades 3 on the side lying opposite the carrier disk 1 are covered by a shroud 4 , which in the embodiment according to FIG. 1 runs out on the inner side into an annular section 5 which forms the run-in of the impeller, as is known per se and is therefore not described in detail.
  • the shape and the arrangement of the blades 3 may be recognized with a removed shroud 4 , as is shown by way of example in FIG. 2 .
  • the impeller according to FIG. 2 as a whole comprises six blades 3 , which have the same shape and size, and are arranged at the same angular distance on the carrier disk 1 .
  • impellers formed of plastic which are manufactured with the injection molding method, as a rule a separate tool is required for each change on the impeller.
  • blades of a different arrangement and size may be provided on an impeller, without increasing the manufacturing costs.
  • the impeller as is the case with a multitude of centrifugal pumps, is formed of sheet metal, typically of stainless steel sheet metal, then different tools are required for different blade shapes, which increases the manufacturing costs.
  • the manufacture itself is effected by way of aligning the individual blades on the carrier disk and these being welding to this, whereupon, as the case may be, the shroud is applied and likewise welded to the blades.
  • centrifugal pumps are offered in different constructional sizes.
  • the size variation is, however, not only varied by way of changing the geometric dimensions and the drive power, but also by way of variation of the blades.
  • an impeller for example, which delivers a certain delivery rate at a given pressure
  • the blade height may be reduced accordingly.
  • natural limits are placed on this, since a minimum passage height must be retained within the impeller in order to ensure fault-free operation.
  • cast impellers it is counted as belonging to the state of the art to fill out intermediate spaces between blade pairs in order to reduce the delivery rate. With impellers manufactured of sheet metal, this is not possible, or only with an increased expense by way of arranging two blades for forming a dead space. However a separate punching tool is necessary for each of these impellers.
  • impeller variance i.e. impellers with different delivery characteristics, which is very favorable with regard to manufacturing technology, and which may be manufactured as inexpensively as possible, in particular of sheet metal.
  • the impeller according to the present invention for a centrifugal pump comprises a carrier disk with blades arranged thereon, with which blades are arranged in pairs next to one another, and at least the blades forming one blade pair have the same shape and size.
  • the basic concept of the present invention is to provide at least one, and preferably several, blade pairs on the impeller, which in each case are arranged next to one another and have the same shape and size.
  • these blades in the end product preferably have the same shape and size.
  • the main concept is, however, to reduce the variance of the blade shape, such that the number of tools for manufacturing the blades may be reduced and moreover the feed of the blades in the manufacturing process and their handling is simplified.
  • the shape and the size of such blade pairs is identical, for example they have the same dimensions and the same radii of curvature.
  • a blade pair forms a flow-effective blade.
  • hydraulically differently effective blades may be formed on the impeller alone by way of the arrangement of the impellers, with two impellers of the same shape.
  • the shape of the blades of such a blade pair according to the present invention is typically designed as is applied with a normal impeller.
  • the variance which may be achieved according to the present invention by way of the paired arrangement of equally shaped impellers is then used for special purposes.
  • such a lengthened blade may be formed by way of two blades of a blade pair, which are applied onto one another in a telescopic manner.
  • Such a lengthened blade may, for example, be applied for a carrier disk of a larger diameter, if an impeller is to be designed for achieving a larger delivery height.
  • an impeller is to be designed for producing a smaller delivery rate.
  • a blade pair consisting of two blades of the same shape and size may be arranged and aligned such that with regard to flow technology, a dead space forms therebetween, if specifically the radial inner end of a blade bears on the other blade and the radially outer ends are distanced.
  • a required multitude of such impeller pairs may be arranged on a carrier disk and that the dead space formed in such a manner is particularly effective if the impeller has a covering shroud.
  • such a dead space may also be formed in a different manner by a blade pair of blades of the same shape and size, if, for example, the radially outer ends bear on one another and the inner ends are distanced, which however as a rule would tend to be less favorable.
  • the present invention may be applied with impellers which are open or covered, and is particularly advantageous with impellers with a covering shroud.
  • the blades of a blade pair may be positioned in a manner such that a blade of the blade pair projects radially beyond the carrier disk and/or the shroud. Hydraulically differently effective blades result by way of this, wherein as the case may be, the projecting ends may be removed in a further manufacturing step, or left as they are.
  • an impeller blade is advantageously dimensioned such that it has a constant height over its entire length. This is particularly advantageous for the paired arrangement, since in this manner one may create particularly good dead spaces, or one may form longer blades.
  • the present invention is especially advantageously applicable to impellers which are manufactured of sheet metal, with which therefore the carrier disk and/or shroud, as well as the blades, are formed of sheet metal and are connected to one another by way of welding.
  • the present invention is, however, not so limited. It may also advantageously be applied to impellers of other materials, for example, of plastics or composite materials, in particular if the carrier disk, shroud and blades are manufactured independently of one another and then joined.
  • FIG. 1 is a greatly simplified schematic perspective view of a centrifugal pump impeller of the prior art
  • FIG. 2 is a plan view of an impeller of the prior art shown without a shroud
  • FIG. 3 is a plan view of an impeller shown without a shroud in accordance with a first preferred embodiment of the present invention
  • FIG. 4 is a plan view of an impeller shown without a shroud in accordance with a second preferred embodiment of the present invention.
  • FIG. 5 is a plan view of an impeller shown without a shroud in accordance with a third preferred embodiment of the present invention.
  • FIG. 6 is a plan view of a modified version of the impeller shown in FIG. 5 .
  • FIG. 3 shows an impeller without a shroud in accordance with a first preferred embodiment of the present invention.
  • the impeller according to FIG. 3 which delivers lower delivery rates than impellers of the prior art (i.e., FIGS. 1 and 2 ), includes two blades 3 a , 3 b that are arranged into an impeller pair, such that hydraulically, a dead space 6 is formed between them.
  • the blades 3 a , 3 b are of the same shape and size, and thus have the same material thickness, the same length, the same height and the same radius of curvature.
  • the blades 3 a , 3 b are, however, arranged in a different manner.
  • the first blades 3 a of the impeller pair are arranged in the same manner as those with the impeller according to FIG. 2 .
  • the second blades 3 b of the impeller pair of FIG. 3 are arranged specifically such that a radially inner end 7 of each second blade 3 b bears on the inner side of a respective first blade 3 a , while radially outer ends 8 of each blades 3 a , 3 b are spaced a predetermined distance apart.
  • FIG. 4 shows an impeller without a shroud in accordance with a second preferred embodiment of the present invention.
  • six impeller pairs in each case consisting of the blades 3 a , 3 b are arranged on a carrier disk 1 .
  • the combined blades 3 a , 3 b do not form a dead space as in the first preferred embodiment of FIG. 3 , but form longer blades.
  • the blades 3 a , 3 b in the second preferred embodiment are applied onto one another in a paired manner and are pulled apart telescopically, such that in comparison to the individual blades 3 a , 3 b of each blade pair, a single, hydraulically effective blade of a greater length results.
  • FIG. 5 shows an impeller without a shroud in accordance with a third preferred embodiment of the present invention.
  • the third embodiment according to FIG. 5 likewise six blade pairs in each case consisting of the blades 3 a , 3 b are arranged on a carrier disk 1 .
  • the first blade 3 a of each impeller pair is arranged radial further to the inside, so that their radially outer ends terminate with the outer periphery of the carrier disk 1 , whereas the outer end of each second blade 3 b of each impeller pair projects beyond this outer periphery.
  • the blades 3 a , 3 b are arranged at a different angle to one another.
  • the blades 3 a , 3 b arranged in pairs on the carrier disk 1 are identical in shape and size, such that they have the same length, the same height and the same radius of curvature.
  • impellers of different hydraulic characteristics while using components of the same shape, which is advantageous since one and the same punching tool may be applied for the blades 3 or 3 a , 3 b . It is to be understood that this is not absolutely necessary.
  • the impeller which has been represented and previously discussed with regard to FIG. 5 , as the case may be, may be machined in a further machining step, in a manner such that the projecting ends of the blades 3 b are removed.
  • the blade pairs which then result, as shown in FIG. 6 , consisting of the blades 3 b ′ and 3 a are then no longer equal in shape and size after this machining step.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/714,626 2009-03-09 2010-03-01 Impeller for a centrifugal pump Active 2032-10-01 US8740569B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP09003369A EP2228541B1 (fr) 2009-03-09 2009-03-09 Roue de rotor pour une pompe centrifuge
EP09003369 2009-03-09
EP09003369.7 2009-03-09

Publications (2)

Publication Number Publication Date
US20100226773A1 US20100226773A1 (en) 2010-09-09
US8740569B2 true US8740569B2 (en) 2014-06-03

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US12/714,626 Active 2032-10-01 US8740569B2 (en) 2009-03-09 2010-03-01 Impeller for a centrifugal pump

Country Status (4)

Country Link
US (1) US8740569B2 (fr)
EP (1) EP2228541B1 (fr)
CN (1) CN101832291B (fr)
TW (1) TWI495795B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120121399A1 (en) * 2009-07-31 2012-05-17 Rem Enterprises Inc. air vacuum pump for a particulate loader and transfer apparatus

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9022742B2 (en) * 2012-01-04 2015-05-05 Aerojet Rocketdyne Of De, Inc. Blade shroud for fluid element
KR101914215B1 (ko) * 2012-04-17 2018-11-01 한화에어로스페이스 주식회사 임펠러의 제조방법
US9599120B2 (en) * 2012-08-24 2017-03-21 Asmo Co., Ltd. Impeller for centrifugal pump and centrifugal pump of vehicle washer device
JP6117659B2 (ja) * 2013-09-06 2017-04-19 本田技研工業株式会社 遠心ポンプ
ITUB20150308A1 (it) 2015-05-04 2016-11-04 Ebara Corp Struttura di girante, particolarmente per pompe centrifughe
DE102016225891A1 (de) * 2016-12-21 2018-06-21 KSB SE & Co. KGaA Freistrompumpe

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US436015A (en) * 1890-09-09 Agitator for stuff-chests
US538050A (en) * 1895-04-23 Half to isaac l
US1947658A (en) * 1931-12-17 1934-02-20 Pizzuto Nicolas Impeller and shaft therefor for use in centrifugal and turbine pumps
US3362338A (en) 1965-01-28 1968-01-09 Armstrong Ltd S A Impellers for centrifugal pumps
GB2168764A (en) 1984-12-22 1986-06-25 Rolls Royce Centrifugal pump impellers
GB2260788A (en) 1991-10-05 1993-04-28 Jaguar Cars Pump impeller
DE4139293A1 (de) 1991-11-29 1993-06-03 Inst Verbundwerkstoffe Gmbh Faserkunststoffverbund-laufrad fuer eine radialstroemungsmaschine
US20030002985A1 (en) * 2001-07-02 2003-01-02 Shu-Chen Tsui Spiral fluted wheel for a pump
US20050242015A1 (en) * 2004-04-30 2005-11-03 Gl&V Management Hungary Kft. Orbital wastewater treatment system with combined surface aerator and submerged impeller

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Publication number Priority date Publication date Assignee Title
GB1510629A (en) * 1974-08-08 1978-05-10 Penny Turbines Ltd N Centrifugal compressor or centripetal turbine
EP0500000B1 (fr) * 1991-02-12 1996-08-14 Comadur S.A. Elément de commande formant souris
SE523740C2 (sv) * 2001-08-27 2004-05-11 Aerodyn Ab Pumpanordning av centrifugaltyp

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US436015A (en) * 1890-09-09 Agitator for stuff-chests
US538050A (en) * 1895-04-23 Half to isaac l
US1947658A (en) * 1931-12-17 1934-02-20 Pizzuto Nicolas Impeller and shaft therefor for use in centrifugal and turbine pumps
US3362338A (en) 1965-01-28 1968-01-09 Armstrong Ltd S A Impellers for centrifugal pumps
GB2168764A (en) 1984-12-22 1986-06-25 Rolls Royce Centrifugal pump impellers
GB2260788A (en) 1991-10-05 1993-04-28 Jaguar Cars Pump impeller
DE4139293A1 (de) 1991-11-29 1993-06-03 Inst Verbundwerkstoffe Gmbh Faserkunststoffverbund-laufrad fuer eine radialstroemungsmaschine
US20030002985A1 (en) * 2001-07-02 2003-01-02 Shu-Chen Tsui Spiral fluted wheel for a pump
US20050242015A1 (en) * 2004-04-30 2005-11-03 Gl&V Management Hungary Kft. Orbital wastewater treatment system with combined surface aerator and submerged impeller

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Office Action issued Aug. 5, 2013 in CN Application No. 201010128895.9.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120121399A1 (en) * 2009-07-31 2012-05-17 Rem Enterprises Inc. air vacuum pump for a particulate loader and transfer apparatus

Also Published As

Publication number Publication date
US20100226773A1 (en) 2010-09-09
CN101832291A (zh) 2010-09-15
CN101832291B (zh) 2015-05-13
TW201033473A (en) 2010-09-16
TWI495795B (zh) 2015-08-11
EP2228541A1 (fr) 2010-09-15
EP2228541B1 (fr) 2012-11-14

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